Low-pressure screw compressor

ABSTRACT

Low-pressure screw compressor provided with a rotor housing ( 2 ) with an inlet side and an outlet side, and enclosing two rotor bodies ( 3  and  4 ) including shafts ( 5, 7  respectively) and screws ( 6, 8  respectively) mounted on the shafts. The rotor shafts ( 5  or  7 ) are bearing-mounted in the rotor housing ( 2 ), with the bearing mountings on the inlet side of the rotor housing each using a single loose bearing and the bearing mountings on the outlet side of the rotor housing each using a single fixed cylindrical roller bearing. Spring devices acting on the bearing mountings at the inlet side urge the shafts and rotors toward the outlet side to maintain minimum clearance between the rotors and the housing at the outlet side of the rotors.

The present invention concerns an improved low-pressure screw compressoror what is called a screw blower.

In particular, the present invention concerns an improved low-pressurescrew compressor which is provided with a rotor housing in which areprovided two engaging rotor bodies which each consist of a shaft and ascrew provided round the above-mentioned shaft, whereby theabove-mentioned rotor bodies are provided in the above-mentioned rotorhousing in a rotating manner as they are bearing-mounted with theirrespective shafts on either side inside the rotor housing.

Low-pressure screw compressors or what are called “screw blowers” arecompressors which are particularly meant to supply a large flow ofcompressed gas at relatively low pressures, in other words pressures ofusually one bar to three bar of relative pressure at the most inrelation to the ambient pressure.

High-pressure screw compressors are already known, whereby for examplethe above-mentioned rotor bodies are bearing-mounted on their inlet sideby means of a single-row cylindrical roller bearing and a four-pointcontact ball bearing, whereas on their outlet side, they arebearing-mounted by means of a single-row cylindrical roller bearing andan thrust bearing.

The presence of the above-mentioned thrust bearing is required with suchknown screw compressors, since considerable axial forces are exerted onthe rotors while such high-pressure screw compressors are operational,such as gas forces and forces coming from driving gear wheels and/orsynchronisation gear wheels.

A disadvantage of such known high-pressure screw compressors is that,because of said bearing arrangement, they are relatively expensive, andthe mounting thereof is considerably time-consuming due to therelatively large number of bearings and the alignment thereof.

Another disadvantage of such known screw compressors is that the bearingarrangement is strongly overdesigned for low-pressure applications.

What are called “Roots blowers” are already known, which are providedwith two engaging rotor bodies which are bearing-mounted in a rotorhousing by means of, for example, a double-row angular contact ballbearing on one side of the rotor housing, and the combination of aspherical roller bearing with either a deep groove ball bearing or acylindrical roller bearing.

Since known Roots blowers have only limited rotational speeds of threethousand revolutions per minute on average to five thousand revolutionsper minute at the most, and the bearings are not loaded by axial forces,such a bearing arrangement is possible, but in the case of low-pressurescrew compressors, which usually work at rotational speeds of sixthousand revolutions per minute or more, the use of the above-mentionedstandard two-row angular contact ball bearings is excluded because ofthe technical restrictions imposed by the bearing manufacturer.

The present invention aims to remedy one or several of theabove-mentioned and other disadvantages.

To this end, the present invention concerns an improved low-pressurescrew compressor which is provided with a rotor housing in which areprovided two engaging rotor bodies which each consist of a shaft and ascrew provided round the above-mentioned shaft, whereby theabove-mentioned rotor bodies are provided in the above-mentioned rotorhousing in a rotating manner as they are bearing-mounted with theirrespective shafts on either side inside said rotor housing, whereby eachof the above-mentioned rotor bodies is bearing-mounted on the inlet sideof the rotor housing by means of a single loose bearing, and on theoutlet side of the rotor housing by means of a single fixed cylindricalroller bearing.

By “cylindrical roller bearings” are meant bearings with a concentricinner and outer ring, in between which are provided rotating rollerelements which are made in the shape of cylindrical rollers.

An advantage of such an improved screw compressor according to theinvention is that, thanks to the use of cylindrical roller bearings,they can be made compact since these bearings have only a limited axialwidth.

Another advantage of such a screw compressor according to the inventionis that it is appropriate for high rotational speeds, in comparison withconventional Roots blowers which make use of angular contact ballbearings.

Another advantage of an improved low-pressure screw compressor accordingto the invention is that it is capable of absorbing large radial forcesand that also axial forces can be absorbed via flanges of suchcylindrical roller bearings.

In a preferred embodiment of a screw compressor according to theinvention, the above-mentioned loose bearing is made in the shape of adeep groove ball bearing, and means are additionally provided which pushone or both rotor bodies to the outlet side of the rotor housing.

By the term “deep groove ball bearing” is meant a bearing which isprovided with a concentric inner and outer ring in which are providedcontinuous grooves opposite each other in between which are providedroller elements made in the shape of round balls.

In practice, such deep groove ball bearings are also called “groove ballbearings” or even, in short, “ball bearings”.

An advantage of such an embodiment of an improved screw compressoraccording to the invention is that, on the outlet side, the tipclearance between the screws and the rotor housing can be minimized, sothat any loss of efficiency can be limited.

In a special embodiment of an improved screw compressor according to theinvention, the above-mentioned means which push one or both rotor bodiesto the outlet side of the rotor housing are made in the shape of aspring which extends between the rotor housing and the screw of thisrotor body.

Such an improved screw compressor is advantageous in that it has asimple construction, and in that the strength of the spring can beselected as a function of the dimensions and the operatingcharacteristics of the screw compressor.

In order to better explain the characteristics of the present invention,the following preferred embodiment of an improved screw compressoraccording to the invention is given as an example only, with referenceto the accompanying drawings, in which:

FIG. 1 schematically represents an improved low-pressure screwcompressor according to the invention in perspective;

FIG. 2 is a section according to line II-II in FIG. 1;

FIGS. 3 and 4 represent the parts indicated in FIG. 2 by F3 and F4respectively, to a larger scale.

FIGS. 1 and 2 represent an improved low-pressure screw compressor 1according to the invention which is provided with a rotor housing 2 withan inlet side and an outlet side, and in which are provided two engagingrotor bodies 3 and 4, a driving rotor body 3 and a driven rotor body 4respectively.

The driving rotor body 3 is built in the known manner in the shape of ashaft 5 around which extends a male screw 6, whereas the driven rotorbody 4 is also formed in the known manner of a shaft 7 around which isprovided a female screw 8 in which the above-mentioned male screw 6engages.

The above-mentioned rotor bodies 3 and 4 can rotate in theabove-mentioned rotor housing 2 as they are each bearing-mounted withtheir respective shafts 5 and 7 on either side inside said rotor housing2.

According to the invention, the above-mentioned rotor bodies 3 and 4 arebearing-mounted on the inlet side of the rotor housing 2 by means of asingle loose bearing 9 which, preferably but not necessarily, is made inthe shape of a single-row, greased, deep groove ball bearing.

By a single-row bearing is meant a bearing in this case which, seen inthe axial direction, is provided with only a single row of rollerelements.

In this case, each of the above-mentioned deep groove ball bearings 9will be loose, as they are provided with an outer ring 10 which isprovided in the above-mentioned rotor housing 2 in such a manner that itcan shift in the axial direction of a respective rotor body 3 or 4.

The respective inner rings 11 of each of the above-mentioned deep grooveball bearings 9 are in this case fixed to a shaft 5, 7 respectively of arotor body 3, 4 respectively.

Between the above-mentioned outer and inner ring 10 and 11 are providedroller elements 12 in the shape of round balls which are usually held inthe known manner in a cage which is not represented in the figures.

If the above-mentioned deep groove ball bearings 9 are greased, thebearings 9 will preferably be sealed in a double-sided manner. Ofcourse, according to the invention, it is not excluded for theabove-mentioned deep groove ball bearings 9 to be oil-lubricated.

As is represented in detail in FIG. 3, the screw compressor 1 is in thiscase, but not necessarily, provided with means 13 which push at leastone and in this case both rotor bodies 3 and 4 to the outlet side of therotor housing 2.

The above-mentioned means 13 are preferably made in the shape of atleast one spring 14 which extends between the rotor housing 2 and therespective rotor bodies 3 and 4, which springs 14 in this case pushindirectly against the rotor bodies 3 and 4 via the outer ring 10 of arespective deep groove ball bearing 9.

On the outlet side of the rotor housing 2, each of the respective shafts5 and 7 of the rotor bodies 3 and 4 according to the invention arebearing-mounted by means of a single, fixed cylindrical roller bearingwhich is preferably but not necessarily made in the shape of asingle-row, oil-lubricated cylindrical roller bearing 15.

According to the invention, it is not excluded for the above-mentionedbearings 9 and/or 15 to be made in the form of two-row or multiple-rowbearings.

As is represented in detail in FIG. 4, the above-mentioned cylindricalroller bearing 15 is in this case made in the shape of what is called aNUP bearing which, in other words, is provided with a fixed outer ring16 provided inside the rotor housing 2 with two fixed flanges 17 whichconfine the runner surface of the roller elements 18.

Such a NUP cylindrical roller bearing is also provided with an innerring 19 which is provided with only one fixed flange 20 against whichthe above-mentioned roller elements 18 are provided with one side edge.

Opposite the other side edge of the above-mentioned roller elements 18of the cylindrical roller bearing 15 is provided a loose, removableflange 21 in case of such a NUP bearing.

In this case, the cylindrical roller bearings 15 are erected such thattheir respective fixed flange 20 are situated on the sides of thecylindrical roller bearings 15 opposite the screws 6 and 8.

However, it is also possible according to the invention for theabove-mentioned cylindrical roller bearing 15 to be made in the shape ofwhat is called an NJ bearing which is not represented in the figures,whereby the outer ring 16 is provided with two fixed flanges 17 and theinner ring 19 is provided with only one fixed flange, but whereby nosecond, loose flange is provided.

An advantage of such NJ bearings is that they are cheaper than theabove-mentioned NUP bearings and that the mounting of such NJ bearingstakes little time, as such bearings are made of several parts, whichstrongly simplifies the dismantling and mounting of the compressors, sothat less man hours are required for manufacturing, maintenance, repairand the like.

In this case is provided round every shaft 5 and 7, between the screw 6,8 respectively and the cylindrical roller bearing 15, a mechanicalsealing 22.

On the other side of the cylindrical roller bearings 15, both shafts 5and 7 of the rotor bodies 3 and 4 extend so as to form two free shaftends which extend up to a sealed room 23 in a transmission housing 24which is provided against the above-mentioned rotor housing 2 or whichis a part thereof.

In the above-mentioned transmission housing 24 is provided round each ofthe above-mentioned free shaft ends a synchronisation gear 25 in thiscase.

On the free end of the shaft 5 of the driving rotor body 3 is in thiscase also provided a gear wheel 26 which engages in a gear wheel 27working in conjunction with it, which is provided on a shaft 28 which iscoupled to a driving motor which is not represented in the figures.

The working of an improved low-pressure screw compressor 1 according tothe invention is very simple and as follows.

By activating the driving motor, via the driving gears 26 and 27, thedriving rotor body 3 is driven, which in turn, via the synchronisationgears 25, drives the driven rotor body 4.

As the screws 6 and 8 engage, an amount of gas is compressed betweenthese screws 6 and 8 in the known manner, which is sucked in on theinlet side of the rotor housing 2 and which leaves the rotor housing 2in a compressed form via the outlet which is not represented.

The freshly drawn-in inlet gas hereby has a cooling effect on theabove-mentioned deep groove ball bearings 9 on the inlet side of therotor housing 2, so that grease lubrication can be applied.

Axial forces which are exerted on the rotor bodies 3 and 4 are absorbedby the above-mentioned deep groove ball bearing 9, as well as by thecylindrical roller bearing 15.

Thanks to the specific bearing arrangement according to the invention,an improved low-pressure screw compressor 1 is much more appropriate forhigh rotational speeds than conventional Roots blowers which make use ofangular contact ball bearings.

The axial driving forces are transmitted by the driving gears 26 and 27,and the gas forces which are created by the compression of the gasbetween the above-mentioned screws 6 and 8 make sure that the rotorbodies 3 and 4 are pushed to the inlet side of the rotor housing 2during the operation of the screw compressor 1.

In the case where use is made of a NUP bearing according to any one ofthe possibilities of the invention, these axial forces can be absorbed,however, by the flanges 17 and 20 of the cylindrical roller bearings 15which prevent their roller elements 18 from moving to the rotor housing2 and which are preferably oil-lubricated to this end.

Since the outer rings 10 of the deep groove ball bearings 9 are providedin the rotor housing 2 in such a manner that they can shift according tothe axial direction of the respective rotor shafts 5 and 7, the forcesexerted on said outer rings 10 by the above-mentioned means 13 aretransferred via the balls 12 to the inner rings 11 which push against acollar 29 of the above-mentioned shaft 5, 7 respectively.

Thanks to the pushing forces of the means 13, the rotor bodies 3 and 4are always forced to the outlet side of the rotor housing 2, also duringthe operation of the screw compressor 1, so that the above-mentionedaxial forces, as a result of the gas compression and possibly of thegear wheel transmissions, are compensated and the fixed flanges 20 and17 of the cylindrical roller bearings 15 are loaded less.

This is of course advantageous to the life of these cylindrical rollerbearings 15 and, as a consequence, the period between two maintenanceservices of such an improved compressor according to the invention isextended.

Another advantage of the presence of the above-mentioned means 13 isthat the tip clearance between the screws 6 and 8 and the rotor housing2 on the outlet side of the rotor housing 2 is always kept to a minimum,so that losses are prevented and the output of the compressor 1increases, and as a result of which the compressor 1 will work in astable manner, also at low outlet pressures.

Another advantage of the above-mentioned means 13 is that the bearing 9cannot shift off the shaft 5; otherwise, an extra locking is required onthe inner or outer ring.

Another advantage of the above-mentioned means 13 is that the bearing 9is pre-stressed, so that there is always the necessary minimal load onthe bearing 9, which guarantees a stable operation.

It is clear that the presence of synchronisation gears 25 according tothe invention is by no means necessary, since the screws 6 and 8 canalso drive each other directly.

Also, it goes without saying that the present invention is notrestricted to oil-free low-pressure screw compressors, but that it canalso be applied in oil-injected low-pressure screw compressors.

It goes without saying that the above-mentioned means 13 which push oneor both rotor bodies 3 and/or 4 to the outlet side of the rotor housing2 according to the invention can be made in may ways, for example in theform of one or several conventional compression springs, one or severalcup springs, one or several leaf springs or any other type of springwhich is suitable.

Moreover, the above-mentioned means 13 according to the invention can bemade for example in the form of a fluid put under pressure, whichtransfers forces, either or not by means of a transmission element, tothe above-mentioned rotor bodies 3 and 4.

According to the invention, the above-mentioned loose bearing is notrestricted to a deep groove ball bearing 9, but in another embodiment itcan also be realised as another type of bearing, such as for example inthe form of a cylindrical roller bearing of the NU type, whereby theinner ring 11 has no flanges and the outer ring 10 is provided with twofixed flanges in between which are provided roller elements 12 in theshape of rollers, or of the NJ type whereby the inner ring 11 has onlyone flange.

The present invention is by no means restricted to the embodiments givenas an example and represented in the drawings; on the contrary, such animproved low-pressure screw compressor 1 according to the invention canbe made in all sorts of shapes and dimensions while still remainingwithin the scope of the invention.

1-10. (canceled)
 11. Low-pressure screw compressor including a rotorhousing having an inlet side and an outlet side; two engaging rotorbodies each including a shaft and a screw provided around each shaftsuch that said rotor bodies are rotatably supported in the rotor housingby said shafts; said shafts being bearing-mounted at each end insidesaid rotor housing; the bearing mounting of each shaft on the inlet sideof the rotor housing comprises a single loose deep groove ball bearingand the bearing mounting on the outlet side of the rotor housingcomprises a fixed cylindrical roller bearing; a spring device locatedbetween the rotor housing and the rotor body arranged to urge one orboth rotor bodies towards the outlet side of the rotor housing, so thata minimum tip clearance between the rotor bodies and the rotor housingon the outlet side is maintained.
 12. Low-pressure screw compressoraccording to claim 11, wherein each said loose deep groove ball bearingincludes an outer ring arranged to be moveable in the rotor housing inthe axial direction of a respective rotor body.
 13. Low-pressure screwcompressor according to claim 11, wherein the cylindrical roller bearingcomprises a single-row cylindrical roller bearing.
 14. Low-pressurescrew compressor according to claim 11, wherein the cylindrical rollerbearing is oil lubricated.
 15. Low-pressure screw compressor accordingto claim 11, wherein the cylindrical roller bearing comprises a NUP-typebearing.
 16. Low-pressure screw compressor according to claim 11,wherein the cylindrical roller bearing comprises an NJ-type bearing. 17.Low-pressure screw compressor according to claim 11, wherein thedeep-groove ball bearing comprise a single-row bearing.
 18. Low-pressurescrew compressor according to claim 11, wherein the deep-groove ballbearing is lubricated by grease.
 19. Low-pressure screw compressoraccording to claim 11, wherein at least one of the deep groove ballbearings is sealed in a double-sided manner.
 20. Low-pressure screwcompressor according to claim 11, wherein each spring device pushesagainst a respective outer ring of a respective deep groove ballbearing.